Apparatus for winding textile material

ABSTRACT

Apparatus for packaging linear material including a driven rotatable collector upon which linear material is wound as a package, means for reducing the angular speed of the collector to keep substantially constant collection speed, a moveable traverse for distributing the linear material on the package, means for sensing the angular speed of the collector as an indication of package size and means responsive to the sensed speed for moving the traverse to keep the traverse in predetermined spaced relation to the package during collection.

' Jan. 29, 1974 J, p KUNK ETAL v APPARATUS FOR WINDING TEXTILE MATERIAL FiledDeo. 8, 1971 4 Sheets-Sheet l Janyze, 1974 J. P. KILINK ETAL r 3,788,826

APPARATUS FOR WINDING TEXTILE MATERIAL.

4 Sheets-Sheet 2 Filed Dec. 8 1971 Jan. 29, 1974 J. RKUNK ETAL Y 3,788,826

A APPARATUS FOR WINDING TEXTILE MATERIAL Filed Dec. 8, 1971 4 VSheebs--Sheet 3 Jan. 29, 1974 Filed Deo. 8

J. P. KLINK ETAL APPARATUS FOR WINDING TEXTILE MATERIAL 4 Sheets-Sheet L United States Patent O 3,788,826 APPARATUS FOR WINDING TEXTILE MATERIAL Jerome P. Klink, Granville, and Phra D. Lyle and Terry L. Griffith, Newark, Ohio, assignors to Owens-Corning Fiberglas Corporation Filed Dec. 8, 1971, Ser. No. 206,007 Int. Cl. B65l1 54/02; C03b 37/02 U.S. Cl. 65-11 W 12 Claims ABSTRACT F THE DISCLOSURE BACKGROUND OF THE INVENTION This invention relates to production of continuous filaments of a thermoplastic material and more particularly to improvements for producing such filaments where production apparatus uses mechanical attenuation of filaments from streams of heated thermoplastic material. The invention is especially useful in producing continuous glass filaments and strands of these filaments.

Normally heated thermoplastic materials such as molten glass are drawn into continuous filaments from streams fiowing from a feeder holding a body of the heated material. Usually apparatus attenuates the streams into individual continuous filaments and combines them into a bundle or strand under the influence of pulling forces exerted directly by a Winder. The Winder collects the strand into a wound package on a collection tube mounted on a driven rotatable collet. The winders commonly used can collect strands at linear strand speeds up to 10,000 to 15,000 feet per minute -or more.

This well known process has inherent shortcomings that influence the filaments, strands and wound packages. For example, the production apparatus uses the winding package itself to provide the attenuating forces. Consequently, repeated wraps of strand on the package with high strand tension gradually builds-up an increasing inward compressive force on the package. This compressive force can crush filaments and buckle interior strand layers. Then too, tension in the strand can bury strand by squeezing strand portions of overlying layers lbetween and below strand portions of underlying layers. The buried strand cannot be freely withdrawn from the package; the entangled strand breaks. Also, the gradual build-up of the winding package effects changes in the strand collection speed for a given rotational speed of the winding collet. The build-up of a package increases its diameter and consequently its circumference. And circumferential surface speed of a winding package equals package circumference times the angular speed of the package. Hence, for a given angular collet speed the strand collection speed (and filament attenuation speed) during package build-up increases towards a maximum speed at the end of a packaging cycle. Under these conditions the filaments are smaller in diameter at the end of a package cycle than they are at the beginning of the cycle. Some packages collect strand for 60 minutes or more. Thus, speed differences (and hence filament diameter differences) can be considerable.

3,788,826 Patented Jan. 29, 1974 ICC There have been attempts to overcome the diliiculties. For instance, special complex collets have been made to apply an outward force against the inward compressive forces of a winding package. Such collets made package removal from collets easier but do not relieve tension within a package. Consequently, the results have been far from satisfactory.

Efforts have been made to overcome filament diameter non-uniformity in filament forming operations by controlling the viscosity of the streams and by attempting to keep a constant linear strand collection speed by varying the collet speed during formation of a package. However, it has only been practical to make these viscosity and collet speed variations in a linear fashion. But the collection speed variations during package build-up change exponentially. Thus, prior efforts have not been fully successful.

Efforts have been made to overcome compressive forces in a package from strand tension and to produce uniform filament diameters by use of pulling Wheels rotated at a constant rotational speed. Here the pulling wheels are between a stream feeder and a collecting device. This prior apparatus uses winders that rotate a collecting package on a collet or spindle with only sufiicient force to take-up strand as strand is made available to it by the pulling wheel. In these prior arrangements a constant torque or constant horse power motor is normally used to rotate the collet. Increased package size (mass) cause these motors to reduce rotational speed and thus the tension in the collecting strands reduces. The apparatus does reduce high strand tensions (compressive forces) in a wound package and produces filaments of uniform tension. But the apparatus does not control tension in a strand.

Further, prior apparatus has lacked stability in high speed strand collection operations. The instability in operation of the apparatus tends to produce linear strand speed variations that jerk strands. Such a situation is particularly harsh on strand in processes using apparatus required to cooperate by matching linear strand speeds. And apparatus producing strand speed changes can be especially disastrous to glass filaments because they are essentially inextensible.

SUMMARY OF THE INVENTION An object of the invention is improved method and apparatus for forming continuous filaments from heated thermoplastic filament forming material such as molten glass;

Another object lof the invention is improved apparatus for forming continuous filaments from heated thermoplastic filament forming material, such as molten glass, and subsequently combining the filaments into a strand and collecting the strand into a wound package at a selected tension.

Yet another lobject of the invention is improved apparatus for matching strand collection speed with a strand feed speed during collection of a 'wound strand package.

Still another object of the invention is improved method and apparatus for processing linear elements.

The above and other objects are attained by apparatus for and method of collecting linear material that includes means for linearly feeding linear material and means for receiving the fed material where one of the means is predeterminedly variable in its linear speed during advancement of the material; the other means is to be matched thereto during advancement of the material. The invention further includes means for sensing the differences between the speeds of the feeding means and the receiving means and means effective in response to the sensed differences between the speeds to change the patterned rate of the control signal to bring the speed of the other means into conformity with actual linear speed of the one means.

Further, the objects embrace use of apparatus for packaging linear material into a wound package that keeps linear material traversing apparatus in predetermined spaced relationship with packages during collection of the packages.

Other objects and advantages will become apparent as the invention is described more clearly in detail with references made to the accompanying drawings.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a front elevation view of apparatus embodying the principles of the invention. FIG. 1 shows a continuous glass filament forming operation where a filament pulling device attenuates glass filaments and a take-up Winder co1- lects glass strand as a wound package.

FIG. 2 is a side elevation view, partially in section, of the apparatus shown in FIG. 1. The section is taken along lines 2-2 in FIG. 1.

FIG. 3 is a back elevation view in section of the Winder shown in FIGS 1 and 2. The section is taken along lines 3-3 in FIG. 2.

FIG. 4 is a plan view of the strand traversing portion of the Winder shown in FIGS. 1 through 3. The dashed lines indicate packages being collected by the Winder.

FIG. 5 is a simple flow diagram of controls used with the apparatus shown in FIGS. 1 and 2.

FIG. 6 is a more detailed, but still simplified showing, of the controls shown in FIG. 5.

FIG. 7 is a somewhat enlarged plan view of the strand engaging transducer or sensor shown in FIGS. 1, 2 and 5.

FIG. 8 is a front elevation view of the transducer shown in FIG. 7 taken along the lines 8 8.

FIG. 9 is a graph showing change in the diameter of a package during collection versus time. The graph generally shows the rate at which a package builds-up during collection.

FIG. 10 is a modified transducer arrangement.

FIG. 11 is an embodiment of controls used to maintain the strand traversing apparatus of the Winder shown in FIGS. 1 through 3 at a predetermined spaced relationship with winding packages.

FIG. 12 is a view in elevation of drive apparatus for moving the strand traversing support of the winder shown in FIGS. 1 through 3.

FIG. 13 is a side elevation view of the apparatus shown in FIG. l2.

IFIG. 14 is a simplified front view in elevation of a continuous glass filament forming apparatus using the winder shown in FIGS. 1 through 3. The Winder is shown without use of a rotary filament pulling device.

FIG. 15 is a side view in elevation of the apparatus shown in FIG. 14.

FIG. 16 is a simple flow diagram of controls for use with the apparatus shown in FIGS. 14 and 15.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The method and apparatus of the invention are particularly valuable in processes forming filaments from heat softened fiber forming mineral material such as molten glass where temperature and filament processing speeds affect fiber diameter. Yet, method and apparatus embodying the principles of the invention are also useful in processing and packaging bundles of textile filaments made from other thermoplastic fiber forming materials. Thus, the disclosed glass fiber forming operation is only an example used to explain the operation of the invention. The invention has wider application in a variety of filament forming operations and processing operations for linear material generally.

The apparatus shown in FIGS. 1 and 2 show a continuous glass filament forming operation embodying the principles of the invention. The apparatus as shown uses a rotary filament pulling device to form continuous glass filaments at a constant filament forming speed. Further,

the apparatus, as shown, combines the filaments into two strands and collects the strands below the rotary pulling device at selected strand tension. Normally such strand tension is less than the sum of the tension in the filaments above the rotary pulling device. The filament pulling device is between a collector and a source of molten glass streams from which the glass filaments are drawn. Hence, the filament pulling device isolates or separates the glass filament forming tension in the filaments above the device from the filaments collected as strands below the device. Associated apparatus introduces a predetermined or selected tension, normally in the range of from 30 to 200 grams, into the glass strands between the filament pulling device and the collector.

The collector matches the strand collection speed with the speed the rotary pulling device feeds the strands to the collector.

The embodiment shown collects two packages; however, one can use the apparatus of the invention to collect one package or more than two packages.

FIGS. 1 and 2 illustrate a container or feeder 10 that holds a body of molten glass. The feeder 10 can receive a continuing supply of molten glass by several known ways. For example, a forehearth can supply molten glass to the feeder 10 from a furnace heating batch materials to molten glass. Also, a melter associated with the feeder 10 can supply molten glass to the feeder by reducing glass marbles to a heat-softened condition. At the ends of the feeder are terminals 12 that connect to a source of electrical energy to heat the feeder 10 by conventional resistance heating. Such heating keeps the molten glass in the feeder 10 at proper fiber-forming temperatures and viscosities. The feeder 10 has a bottom 14 with orifices or passageways for delivering streams 16 of molten glass from the feeder 10. As shown depending orifices projections or tubular members 18 define the openings in the bottom 14.

The feeder is normally made of platinum or an alloy of platinum.

The molten glass streams 16 are attenuated downwardly into individual continuous glass filaments 20. Gathering shoes 22 and 24 below the feeder 10 combine .the continuous glass filaments 20 into two bundles or strands 26 and 18 respectively.

Normally apparatus applies both water and a liquid sizing or other protective coating material to the filaments 20. As shown nozzles 30 and 32 adjacent to the bottom 14 of the feeder 10 direct Water spray onto the continuous glass filaments 20 before the shoes 22 and 24 combine the filaments 20 into the glass strands 26 and 28.

A sizing applicator 36 supported within a housing 38 just above the gathering shoes 22 and 24 applies a liquid sin'ng or other coating material to the swiftly traveling continuous glass filaments 20. The applicator may be any suitable type of applicator known to the art; however, the applicator 36 is shown as an endless belt moved through liquid held in the housing 38. As the continuous glass filaments 20 speed in touching relationship across the surface of the moving endless belt applicator 36, some of the liquid on the surface transfers to them.

A pulling wheel 40 attentuates the continuous glass filaments 20 at a constant speed from the molten glass streams 16 supplied by the feeder 10. The pulling wheel 40 is rotatably mounted on a housing 42 located just below the shoes 22 and 24. A motor 44 within the housing 42 rotates the pulling wheel at a constant high angular speed. In practice the motor 44 is normally an induction motor.

The pulling Wheel 40 is normally about l2 inches in diameter. The motor 44 can rotate the wheel 40 sufficiently fast to withdraw the continuous glass filaments 20 from the streams 16 at linear speeds up to 12,000 feet per minute and faster.

As shown in FIGS. 1 and 2 the strands 26 and 28 proceed from the shoes 22 and 24 over a strand alignment shoe 46 having circumferential grooves 48 and 4l9 into contact with a smooth circumferential surface 45 of the pulling wheel 40. The shoe 46 aligns the paths of the traveling strands for spaced apart mutually parallel relationship on the smooth circumferential surface 45 of the pulling wheel 40, the strands being disposed substantially parallel to the circumferential center line of the pulling wheel 40. In FIG. l the strands 26 and 28 come into contact with the pulling wheel 40 at the right hand side of the wheel 40 and leave the Wheel at its left hand side.

The alignment shoe 46 is somewhat to the right and above the pulling wheel 40.

From the pulling wheel 40 the strands 26 and 28 advance upwardly and turn over the top of a spool or roller 54 rotatably mounted on the end of an arm 56. The arm 56 is pivotally mounted on the housing 42. In FIG. l the roller 54 and arm 56 are somewhat above and slightly to the left of the pulling wheel 40. A spring 58 within the housing 42 biases the arm 56 in a clockwise direction as viewed in FIG. 1. The biasing force of the spring 58 introduces selected tension into the traveling strands 26 and 28. The introduced tension is selected to permit the build of desired stable wound packages.

The locations of the alignment shoe 46 and the roller 54 promote non-slipping engagement between the Wet traveling strands 26 and 28 and the speeding peripheral surface 45 of the pulling wheel 40'. Normally an engagement of the strands along from 601 to 80 percent of the length of the peripheral surface 45 is sufiicient to insure non-slipping engagement between the surface 45 and the wet strands 26 and 28. Angle A in FIG. 1 represents the angular engagement of the strands 26 and 28 along the peripheral surface 45 of the wheel 40. Angle A is normally from 240 to 300 degrees; an angle of from 250l to 280 degrees is normally preferred for pulling wheels having a diameter of 1l to 12 inches.

To promote non-slipping engagement between the wet strands 26 and 28 and the pulling wheel 40, the wheel 40 as shown uses an annular layer 60 of polyurethane. The layer 60 forms the smooth circumferential surface -45 of the wheel 40. At times it can be useful to control the surface finish, e.g. to somewhat roughen the circumferential surface 45, to enhance engagement between the surface and the wet strands.

The diameter of the pulling wheel 40 and the increased non-slipping engagement from a surfacing layer like layer 60 enhances the non-slipping lament pulling capacity of the wheel 40, which can be used in lament forming operations having ilament forming tensions as high as 700 grams or higher. Filament forming tension is the total or summation of tension in each of the filaments 20l above the applicator 30.

The pulling wheel 40 feeds the strands 26 and 28 at a constant linear strand speed to a winder 70 below. 'Ihe strands travel from the pulling wheel 40 across the roller 54 and strand alignment shoes 62 and 64 to the winder 70.

The Winder 70 collects the strands 26 and 28 as essentially identical wound packages 72 and 74 respectively on collectors. These collectors are shown as tubes 76 and 78 telescoped over a spindle or collet 80. A drive within the Winder 70l rotates the collect 80.

Strand traversing apparatus 82 of the Winder 7 0= reciprocates the strands 26 and 28 back and forth lengthwise of the packages 72 and 74 (collet 80) to distribute the advancing strands on their respective packages during package formation. Strand movement effected by the strand traversing apparatus 82 is a combination of a fast primary strand reciprocating motion and a slower secondary strand reciprocating motion.

One can better understand the strand traversing apparatus 82 by looking at the apparatus shown in FIGS. 1 through 4. The strand traversing apparatus 82 includes strand guides 88 held in spaced relation adjacent to the packages 72 and 74 by a support arrangement. The guides 88 slide in a slot lengthwise of a horizontally extending tubular cam support housing projecting from the frame 92 of the Winder 70. Rotatably mounted within the support housing 90 are identical co-axially joined together cylindrical or barrel cams 96 with surface guide grooves 98. Cam followers 100 connect the strand guides 88 with the grooves 98 of the barrel cams 96. As the cams 96 r0- tate, the strand guides 88 reciprocate along the slot in the housing f90 lengthwise of the collet 80 (packages 72 and 74). As shown the cam support housing l90' and the cams 88 extend co-axially. And the housing 90 extends in a direction parallel to the collet 80 with its axis in the same horizontal plane with the axis of the collet 80.

As shown the strand guides 88 are hooked at their ends to keep the strands 26 and 28 engaged.

As the cams 96 reciprocate the strand guides 88, the guides reciprocate the strands 26 and 28 lengthwise of the collecting packages 72 and 74.

The Winder 7 (l includes a drive arrangement comprising a motor/clutch 102 within the Winder housing 92. The drive arrangement effects rotation of the cams i96 and rotation of the collect 80 at a controlled speed ratio. The desired package design determines the ratio.

The motor/clutch drive i102 includes a constant speed electric motor 104 that drives the rotor of an associated eddy-current clutch 106. The clutch 106 has an output shaft 108. Magnetic forces within the clutch 106 transfer torque from the rotor driven by the motor 104 to the output shaft 108. In practice the motor 104 s an induction motor.

The motor/ clutch 102 is a variable speed drive. In operation the speed of the motor 104 remains constant; however, changes in flux density (magnetic forces) within the clutch 106 vary the amount of the motors constant speed rotational energy output transferred to the output shaft i108. The greater the ilux density the larger is the percentage of motor output transferred to the output shaft 108.

The drive 102 rotates the collet 80 through a non-slipping belt 110 connecting the output shaft 108 with a collet drive shaft 112 above the drive 102. The rotating collet drive shaft 112 rotates the collet 80. The shaft 1-12 is co-axial with the collet 80 and is rotatably held by a bearing mounting assembly 114.

Rotational energy from the collet drirve shaft 112 moves the strand traversing apparatus 82 through non-slipping belts 116 and 118. The belt 1116 connects the collet drive shaft 112 and a rotatably mounted idler shaft 119 of an idler assembly 120. The belt 118 connects the idler shaft r119 with a cam drive shaft 124 that connects to and rotates the cams 96. The drive shaft 124 is co-axial of the cams `96 and is rotatably mounted by a bearing support assembly 126 and the vertical end plate 128 of a movable carriage 130.

As the packages 72 and 74 build on the rotating collet 80, the diameter of each of the packages increases. And for any given angular collet speed an increase in package diameter increases the speed of the circumferential or axial surface of each of the packages 72 and 74. Hence, the strand collection speed would increase with increasing package diameter if there were no olfsettingreduction in the angular speed of the collet 80.

Accordingly, the invention includes means for controlling the angular speed of the collet 80 to offset increases in strand collection speed from increasing package size during strand collection. As shown, controls modify collet speed through the drive 102. Such controls are effective to maintain a strand collection speed equal to the constant strand supply speed from the rotating pulling wheel 40 throughout build-up of the packages 72 and 74.

The controls include means for establishing a control signal effective to modify the rotational speed of the collet 80 in accordance with a patterned rate of change that, in general, will effect a package build-up at a linear strand speed matched to the speed of strand feed. The controls further include means for sensing the dierences between the linear rate of supply and linear rate of collection and means effective in response to such sensed speed dilferences to modify the patterned rate of change of the control signal to bring the linear rate of strand collection into conformity with the actual linear rate of strand supply from the pulling wheel 40 throughout buildup of the packages 72 and 74. 'Ihe result is a substantially constant linear strand collection speed throughout build of the packages 72 and 74.

Thus, in a broad sense, the invention includes means for linearly feeding linear material and means for receiving the fed material where one of the means (either the feeding means or the receiving means) is predeterminedly variable in its speed during advancement of the material and the other means is to be matched thereto. To effect the matching the invention includes control means supplying a control signal having a patterned rate of change that is effective to modify the speed of the matching speed means to approach in general the speed of the predeterminedly variable speed means. Further, the invention provides means for sensing the differences between the speeds of the feeding means and receiving means and means effective in response to the `sensed speed differences to change the patterned rate of the control signal to bring the matching speed means into conformity with the actual speed of the predetermined variable speed means.

FIG. shows a general block diagram embodiment of controls according to the principles of the invention. In the embodiment a controller 140 varies voltage signals to the eddy-current clutch 106 to control the rotational speed of the collet i80- during collection of the wound packages 72 and 74. In the embodiment the controller 140y receives voltage signals from a sensing transducer 142 and receives a constant DC voltage signal from a suitable DC source such as a battery 144. The changing output voltage of the controller 140 controls the magnetic eld strength of the eddy-current clutch 106 to effectively match the strand collection speed with the strand supply speed as the packages 72 and 74 increase in diameter. For improved stability the controller 140 receives feedback voltage signals from a tachometer 146; the tachometer signals are a measurement of the actual angular lspeed )of the clutch output shaft 108 (and hence the col- Referring to FIG. 6, the controller 140` includes an integrator 150, a major summing junction J1, and an amplitier 154. The integrator 150 includes resistance 156 in a line 158, an operational amplifier 160 and an integrating capacitor 162 bridged between the input and output of the operational amplifier 160. A line 164 connects the output of the operational amplifier 160 (integrator 150) with the summing junction I 1. A line 166 connects the summing junction J1 with the amplifier 154. A package build switch 167 is in the line 164 between the junction I1 and the integrator 150.

The battery 144 supplies a constant voltage to the summing junction J1 through a line 168.

The tachometer 146 supplies its signal to the summing junction J1 through a voltage divider 170, e.g. a poteniometer, in a line 171. The setting of the voltage divider 170 establishes the operating rotational speed of the collet 80 at the start of package build.

The voltage from the summing junction J1 in line 166 is the algebraic summation of all the voltages supplied to the junction J1. As illustrated the voltage applied to junction I1 by the battery 168 is positive; the voltage applied to junction l1 by the integrator 150 is a generally increas ing negative voltage; the voltage applied to junction Il by the tachometer 146 is a negative voltage.

The increasing negative voltage from the integrator 150 reduces the voltage from the junction J1 (the controller 140) throughout the build-up of the packages 72 and 74. Hence, the reducing voltage from the controller 140 correspondingly reduces the rotational speed of the collet 80 during package collection.

The amplifier 154 amplies the voltage signals from the junction J1 to put them at proper strength for use by the eddy-current clutch 106.

'Ihe integrator 150 provides a steadily changing electrical output signal that increases proportionately to the negative time integral of input voltage. Hence, for a given constant input voltage the integrator supplies an output voltage that has a polarity opposite to the input voltage and that builds (increases) linearly with respect to time. Accordingly, for a given constant positive input voltage the output voltage from the integrator 150 increases in a negative direction at a constant rate of change. For different positive input voltages the linear rate of change of the integrator output voltage can be made rapid (a steep slope) with respect to time or made to be slower (a more gradual slope) with respect to time. For exam ple, larger positive integrator input voltages produce higher rates of output voltages change (a steeper slope) in the negative direction.

During package collection the transducer 142 supplies changing input voltages to the controller 140 from a junction J2 through line 158. The junction J2 receives negative DC voltage through a potentiometer 175 in line 176; negative voltage from a suitable source is applied to the line 176 at L1. The junction J2 receives positive DC voltage in line 178 through a resistance 179; positive voltage from a suitable source is applied to the line 178 at L2. The voltages from L1 and L2 oppose each other, and there is no input voltage to the controller 140 when the voltage effected at junction I2 is zero with respect to ground.

In the embodiment shown the transducer 142 includes the junction J2, potentiometer 175, the pivotally mounted arm 56 and its spool or roller 54. The transducer 142 can be more fully understood by considering FIGS. 7 and 8 together with FIG. 6. As shown the potentiometer 175 within the housing 42 has a control shaft 182. The shaft 182 extends through the wall 184 of the housing 42 and holds the arm 56. The arm 56 is fixed on the shaft 182. Hence, any pivotal movement of the arm 56 moves the shaft 182 about its axis and accordingly modifies the output voltage of the potentiometer 175.

The biasing force of the spring 58 urges the arm 56 to pivot about the shaft 182 in a clockwise direction (as viewed in the figures) into the strands 26 and 28 turning on the roller or wheel 54. As shown a lever arm 188 is fixed at one end to the potentiometer control shaft 182. The lever arm 188 extends from the control shaft 182 in a direction opposite to the arm 56. The spring 58 connects to the lever arm 188 and produces a torque in the control shaft 182 urging the arm 56 into the strands 26 and 28. Thus, the arm 56, shoe 54 and biasing arrangement form a sensor that engages the strands 26 and 28 to sense the relationship between the strand collection and feed speeds.

The transducer 142 has a no output voltage position for the arm 56 where no current signals flow from the juntion J2. In such a position the output voltage from the potentiometer 175 and the DC voltage supplied to the junction J2 from L2 effect a zero voltage at I2. In practice a horizontal position from the arm 56 has provided a satisfactory no output voltage position for the transducer 142. Other no output voltage positions can be used.

As the arm 56 is moved progressively downwardly from the horizontal, the potentiometer 175 is arranged to give smaller negative output voltages. Consequently, an increasing positive voltage is applied to the line 158 as the arm 56 moves progressively downwardly.

When the arm 56 moves above the horizontal position, the size of the voltage applied at L1 is sufficient to produce a negative voltage from the potentiometer 175 larger in magnitude than the positive voltage applied at L2. Hence, when the arm 56 is above the horizontal position, negative current is applied to the line 158 from the junction J2. Normally the arm remains below the horizontal during package build-up. Thus, the current applied to the line 158 is normally positive.

In operation the transducer 142 senses the relationship between the strand feed rate of the pulling wheel 40 and strand collection rate of the winder 70 and includes means that provides a signal in response to the sensed differences between the rate of feed and rate of collection of the material. When the strand collection speed is greater than the strand supply speed, the length of the strands 26 and 28 shortens between the pulling wheel 40 and the packages 72 and 74. Hence, the strands 26 and 28 pull the arm 54 downwardly (counter clockwise). The negative voltage from the potentiometer 175 becomes smaller. A larger positive voltage is supplied to the controller 140 from the junction I2. On the other hand, when the strand collection speed is less than strand supply speed, the length of the strands 26 and 28 increases between the pull wheel 40 and the packages 72 and 74. Hence, the stands 26 and 28, in a sense, develop slack that permits the biasing force of the spring 58 to move the 'arm 56 upwardly. The negative voltage from the potentiometer 175 becomes larger in magnitude. Accordingly, a smaller positive voltage is supplied from the junction I2 to the controller 140.

In operation at the beginning of package build, the axial surfaces of the collectors 76 and 78 and the pulling wheel 40 are brought up to equal speeds with switch 167 open. The switch 167 is closed and the build of the packages 72 and 74 begins. Immediately their diameters begin to increase. And consequently the strand collection speed begins to accelerate beyond the strand supply speed from the pulling wheel 40. Quickly the accelerating strand speed shortens the lengths of the strands 26 and 28 between the pulling wheel 40 and Winder 70. The shortening strand length pulls the arm 56 downwarly below the horizontal until the positive voltage from the transducer 142 to the integrator 150 causes the integrator 150 (controller 140) to provide a control voltage signal having a patterned rate of change with respect to time that reduces the speed of the collet 80 (through the eddy-current clutch 106) in accordance with the build-up of the package at that moment. In this initial equilbrium condition the reducing angular speed of the collet 80 keeps the strand collection speed matched to the strand supply speed from the pulling wheel 40. In other words, the patterned rvoltage signal from the controller 140 resulting from the initial equilibrium voltage supplied by the transducer 142 is effective initially to keep the collection speed of the strands 26 and 28 equal to the supply speed from the pulling wheel 40.

But the initial voltage output from the controller 140 reduces linearly with respect to time and the build-up of the packages 72 and 74 increases strand collection speed nonlinearly. Hence, the initial linear voltage pattern from the controller 140 (established by the initial equilibrium voltage supplied by the transducer 142) is only in general accordance with the build-up of the packages. Thus, matching strand collection and strand supply speeds is only temporary.

Package build is shown in FIG. 9. As one can seen the build-up of the packages 72 and 74 is the most rapid when package build begins. Package build-up slows as the packages 72 and 74 become larger in diameter. -In practice, it has been found that the changes (increases) in package diameter during package build occur in a complex nonlinear manner having both parabolic and exponential characteristics. Hence, the curve illustrated in FIG. 9 has both exponential and parabolic characteristics.

Hence, the linear voltage slope from the controller 140 (integrator 150) established by the initial equilibrium transducer voltage is steeper than required to keep the strand collection speed equal to the strand supply speed. Therefore, the strand collection speed quickly becomes slower than the strand delivery speed from the pulling 10 wheel 40. Slack develops in the strands 26 and 28 that permits the biasing force of the spring 58 to move the transducer arm 56 upwardly. Such upward movement of the arm 56 reduces the positive voltage from the transducer 142 until a new equilibrium condition exists. That is, the arm 56 is permitted to move until the slope of the voltage from the controller 140 (integrator 150) matches the rate of collet speed reduction with the rate of package build-up at that moment.

Throughout build of the packages 72 and 74 equilibrium conditions are repeatedly established. In the embodiment shown equilibrium conditions are, for practical purposes, being continuously established. Under such conditions the positive voltage from the transducer 142 to the controller 140 reduces throughout package build up and the slope of the controller output voltage continuously changes from an initial steep slope to more gradual slopes.

In a sense one may consider the controls providing instantaneous control voltages changing with instantaneous rates of change matched with instantaneous accelerations in the strands 26 and 28 throughout package build. These control signals are effective to change the patterned rate of change of the control signal to maintain a substantially constant collection speed equal to the strand feed from the pulling wheel 40.

The summation of all the instantaneous voltage slopes from the controller 142 plots a curve in conformity with the curve of diameter change with respect to time as shown in FIG. 9.

If necessary the controls can keep stable operation during times an increase in rotational speed of the collet is needed. Such a situation occurs during times the collection speed is considerably below the feed speed from the pulling wheel 40. Slack in the strands 26 and 28 allows the biasing force of the spring 58 to move the arm 56 above its no voltage signal position (above the horizontal). A negative current ows in the line 150. The growing negative integrator output signal is reduced. The output voltage from the controller increases, which effects an increasing angular collet speed.

Normally an increase in angular speed of the collet 80 is not necessary. Hence, it is believed possible to use a transducer 142 as shown in FIG. 10. In the arrangement the potentiometer supplies a positive voltage (applied across L3 and L4) directly to the controller 140. A transducer like the transducer 142 is preferred.

It is believed possible to use other means for providing a control signal changing generally in accordance with the build-up of packages like packages 72 and 74. For example, one might use an R-C circuit having a condenservoltage curve for a given voltage changing at a patterned rate generally corresponding to the build-up of the packages. Means such as a transducer 142 and 142 would supply control signals to the R-C circuit in response to sensed speed differences between the strand supply and collection speeds to modify the reference voltage. Also, one might control the amplifier section of an integrator circuit in response to sensed speed differences effective to modify amplification of an input voltage to provide a changing output signal that effects a constant strand collection speed.

One might use other transducers. For example, one might use a transducer engaging the traveling strands 26 and 28 between the wheel 40 and Winder 70 to sense tension as an indication of the differences in the strand delivery and collection speeds. One might use a transducer like the transducer disclosed in U.S. Pat. 3,526,130.

The invention envisions a sensor for indicating the differences in strand collection and delivery speeds that does not engage the strands. For example, it is believed possible to use a Doppler shift laser to measure differences in the circumferential surface speeds of the pulling wheel 40 and the packages 72 and 7 4.

The embodiment shown uses the pulling wheel 40 to feed strands at a constant speed to the Winder 70; however, the invention envisions other embodiments where the pulling wheel 40 or another strand feeding means supplies strands at various speeds. In such situations the controls operate to match strand collection speed with various strand feed speeds during package collection. Also, the invention embraces the use of the controls for matching the delivery speed of linear material with changing collection speeds of the material, e.g. rotating the collet 80 at a constant angular speed throughout package build.

The winder 70 senses the angular speed of the collet 80 as an indication of the size of the packages 72 and 74 during collection and includes means responsive to sensed angular speed for elfectively moving the strand traversing apparatus 82 away from the collet 80 to maintain the traversing guides 88 in predetermined spaced relation to their respective packages throughout collection of the packages. The hooked guides 88 move the engaging strands 26 and 28 with them as the hooks move with the support arrangement during collection of the packages.

Controlling the relationship between the packages 72 and 74 and strand traversing apparatus promotes improved strand control throughout package build and hence improved package build.

As more clearly seen in FIGS. 2 and 3, the carriage 130 is movable on the Winder 70. And the cam housing 90 is carried by the carriage 130. Hence, the housing 90 moves with the carriage 130. The cam housing 90 and carriage 130 move horizontally.

As shown the Carriage 130 includes a base 190 in addition to the vertical end plate 128. The carriage 130 slides lengthwise on two horizontal parallel support rods, rod 192 and 194, that are stationary within the Winder 70. These rods extend through passageways in the base 190; the passageways extend in a direction perpendicular to the axis oft the collet 80 (packages 72 and 74). Hence, the carriage 130 and cam housing 90 are movable in a horizontal plane towards and away from the collet 80 in a direction perpendicular to the axis of the collet 80. The

Winder frame 92 includes an elongated opening 191 permitting movement of the strand traversing apparatus 82 (cam housing 90).

FIGS. 11 through 14 show controls for positioning the carriage 130 throughout package build-up to keep a predetermined spaced relationship between the packages 72 and 74 and the strand traverse guides 88. A switch 198 completes the control circuit. The switch 198 can be manually closed to complete the circuit or automatically closed to complete the circuit when the collet 80 arrives at operating speed to begin package collection. Referring to FIG. 11, a battery 200 supplies a constant positive DC voltage to a potentiometer 202. The output voltage of the potentiometer 202 travels to a summing junction I3 through a lead 204. The tachometer 146 provides a negative DC signal to the junction J3 through a lead 210. When the voltages supplied to the junction I3 are unbalanced, the junction J3 supplies an electrical signal through an output lead 212 (through switch 198) to a grounded solenoid coil or electromagnet 216 that operates to close a normally open armature switch 218. The switch 218 is in a circuit supplying electrical energy to a motor 220; a suitable commercial electrical source supplies electrical energy to the circuit across L3 and L4. The motor 220 is energized when the armature 218 is closed.

The energized motor 220 concurrently drives the slider of the potentiometer 202 and actuates a drive system that moves the carriage 130.

When the voltage from the potentiometer 202 and the tachometer 146 are equal, there is no electrical output from the junction J3; hence, the armature switch 218, which is normally open, remains open. As the voltage from the tachometer 246 decreases from the decreasing angular output speed of the clutch 106, the solenoid coil 216 becomes energized ffrom the higher voltage into the junction J3 from the potentiometer 202. The coil 216 closes the armature switch 218; and the motor 220 effects movement of the slider of the potentiometer 202 to reduce potentiometer output voltage until the output voltage is equal to the output voltage from the tachometer 146. The solenoid coil 216 then becomes de-energized. The armature switch 218 opens and the motor 220 becomes de-energized.

FIGS. 12 and 13 show more of the strand traverse position control apparatus in a control box 224 mounted on the base 190 of the carriage 130. Mounted near the top of the control box 224 is the electric motor 220 with a sheave 226 on the output shaft 228 of the motor 220. Mounted below the motor 220 in the control box 224 is the potentiometer 202 with a sheave 230 on a slider control shaft 232 of the potentiometer. `At the bottom region of the control box is a carriage drive including a rotatably mounted drive screw 236 in a threaded passageway 238 in the hase 190 of the carriage 130. An unthreaded portion 242 of the drive screw 236 carries sheaves 244 and 246.

The energized motor 220 rotates the drive screw 236 and moves the slider of the potentiometer 202. A belt riding in sheaves 226 and 244 connects the motor output shaft 228 with the drive screw 236. A belt 252 riding in sheaves 230 and 246 connect the drive screw with the slider control shaft 232.

As the motor 220 rotates, the slider control shaft 232 moves the slider of the potentiometer 202 and the drive screw 236. The rotating drive screw 236 moves the carriage 130 away from the collet 80 (collecting packages) until the potentiometer voltage equals the voltage from the tachometer 146. The coil 216 then becomes de-ener gized; the switch 218 then opens to de-energize the motor 220.

In practice the motor 220 is a slow r.p.m. motor as S10- Syn made by the Superior Electric Company.

An operator can select a desired position relationship between the guides 88 and collecting packages, e.g. packages 72 and 74. Because the collet speed at the beginning of package collection is controlled and hence known, an operator can adjust a trim potentiometer 260 to bring the voltage from the potentiometer 202 into balance with the known beginning voltage from the tachometer 146. Hence, the operator moves the cam housing 90 (carriage 130) to a selected location to position the guides 88. Such movement also moves the slider of potentiometer 202. Thus, the operator merely adjusts the trim potentiometer 260 to provide voltage from the potentiometer 202 at the beginning of package build-up that matches the tachometer voltage.

The idler assembly permits movement of the carriage without parting the drive belts 116 and 118. As shown the idler 120 includes the rotatable idler shaft 119, bearing box 270, position arm 272, support member 274 and support bracket 276.`

The support member 27,4 and bracket 276 hold the bearing box 270 and shaft 119 above the carriage 90. The bearing box 270 is movable about the axis of the support member 274 by swing legs 277 and 278.

The position arm 272 connects the shaft 119 and cam drive shaft 124 to keep these shafts at a constant spaced distance from the belt 118. The arm 272 pushes (swings) the shaft 119 and its gear box upwardly around the axis of shaft support member 274 as the carriage 130 moves towards the colletY 80. The reverse is true as the carriage 130 moves away from the collet 80.

The swinging movement of the assembly 120 keeps both the belts 116 and 118 in driving relationship on their respective sheaves.

The winder 70 provides for the slower secondary strand traversing motion by apparatus reciprocating the cam housing 90. Such apparatus includes a motor 280, spur gears 282 and 284, cam 286 and follower 288. In the embodiment shown, the cam 286 is a wheel cam xed on a rotatable shaft 290. The motor 280 rotates the wheel cam 286 through the meshing spur gears 282 and 284. 'I'he follower 288 includes a pin 292 engaging the peripheral groove 294 on the Wheel cam 286. The follower 288 is secured on the cam drive shaft 124. As the shaft 290 turns the wheel 286, the wheel reciprocates the follower 288. Hence, the cam wheel 286 reciprocates the cam housing 90 through the follower 288. A conventional spline arrangement (not shown) can be used to permit the shaft 124 to move back and forth along its axis and still be driven in rotation.

One can use various cam 'wheels to provide secondary strand traversing motions having different stroke lengths. In the embodiments shown in FIGS. 1 and 2. it has been useful to use a short secondary reciprocating stroke length of from 1/2 inch and less.

The Winder 70 is shown in combination with apparatus for modifying the angular speed of the collet 80 (packages 72 and 74) exponentially. But the Winder 70 can be used with apparatus modifying the angular speed of the collet 80 in a linear fashion. Moreover, the Winder 70 can be used to pull linear elements from a source, e.g. pull glass strands without the use of a lament pulling device like the pulling Wheel 40.

FIGS. 14 and 15 illustrate the Winder 70 without a pulling arrangement above it. As shown a feeder 310 supplies molten glass streams 316 from tips 318. The Winder 70 withdraws continuous glass filaments 320 from the streams 316. Gathering shoes 322 and 324 combine the filaments 320 into two strands, i.e. strands 326 and 328. A sizing applicator 336 held in a housing 338 applies liquid sizing or other coating material. The strands 322 and 324 wind as packages 372 and 374.

In the embodiment shown in FIGS. 14 and 15 one can use known ways to modify the speed of strand collection as the packages 372 and 374 increase in size. FIG. 16 shows a control using the controller 140 without a transducer. In FIG. 16 a source of DC voltage 380 supplies a constant voltage input'to the integrator 150.

We claim:

1. Apparatus for packaging linear material comprising:

a rotatable collector for collecting linear material as a wound package;

means for rotating the collector;

means for modifying the angular speed of the collector in accordance With the changing size of the package during package formation;

a movably mounted traverse means for reciprocating the linear material axially of the package to distribute the material thereon;

means for sensing the angular speed of the collector as an indication of the size of the package during collection; and

means responsive to the sensed angular speed for moving the traverse means to effectively maintain the traverse means in predetermined spaced relation to the package during package formation.

2. Apparatus for packaging linear material comprising:

a rotatable collector for collecting linear material as a wound package;

means for rotating the collector;

means for modifying the angular speed of the collector in accordance with the increasing size of the package during collection;

a movably mounted support;

a traverse guide carried by the support;

means for reciprocating the traverse guide axially of the collector for distribution of the linear material on the package;

means for sensing the angular speed of the collector as an indication of the size of the package during package formation; and

means responsive to the sensed angular speed for moving the support away from the circumferential surface of the package to maintain the traverse guide in spaced relation to the package during formation of the package.

3. Apparatus for packaging linear material comprising:

a collector rotatably mounted on a fixed axis for collection of linear material as a wound package;

means for rotating the collector;

means for reducing the angular speed of the collector in accordance with increasing diameter of the package during collection;

a movably mounted support;

a strand traverse guide mouted for movement axially of the collector on the support;

means for reciprocating the traverse guide for distribution of the linear material on the package;

means for continuously sensing the angular speed of the collector as an indication of the increasing diameter of the package during collection; and

means responsive to the sensed angular speed for moving the support Way from the axial surface of the package to maintain the traverse in spaced relation to the axial surface of the package during collection of the package.

4. Apparatus for packaging linear material comprising:

a rotatable collector for collection of linear material as a wound package; y

means for rotating the collector;

means for modifying the angular speed of the collector in accordance with the increasing size of the package during collection;

a movably mounted support;

a traverse guide on the support, the support being movable in a direction perpendicular to the axis of the collector;

means for reciprocating the traverse guide axially of the collector for distribution of the linear material on the package;

means for sensing the angular speed of the collector as an indication of the size of the package during collection; and

means responsive to the sensed angular speed for moving the support away from the axial surface of the package to maintain in the traverse guide in predetermined spaced relation to the axial surface of the package throughout formation of the package.

5. Apparatus for packaging linear material comprising:

a collector rotatably mounted on a xed axis for collection of linear material as a wound package;

means for rotating the collector;

means for reducing the angular speed of the collector in accordance with the increasing diameter of the collecting package;

a carriage mounted for movement in a direction perpendicular to the axis of the collector;

a cam housing on the carriage extending in a direction parallel to the axis of the collector;

a rotatable cylindrical cam in the cam housing;

a strand traverse guide slidably mounted on the cam housing for movement axially of the collector, the strand traverse guide engaging the cylindrical cam;

means for rotating the cam for reciprocation of the traverse guide to distribute the linear material on the package;

means for continuously sensing the angular speed of the collector as 'an indication of the increasing diameter of the package during collection and providing electrical signals proportionate to the sensed speeds; and

means responsive to the electrical signals for moving the carriage away from the axial surface of the package to maintain the strand traverse guide in predetermined spaced relation to the axial surface of the package during formation of the package.

6. Apparatus for packaging linear material comprising:

a collector rotatably mounted on a fixed axis for collection of linear material `as a wound package;

means for rotating the collector;

means for reducing the angular speed of the collector in accordance with the increasing diameter of the collecting package;

a carriage mounted for movement in a direction perpendicular to the axis of the collector;

a cam housing on the carriage extending in a direction parallel to the axis of the collector;

a rotatable cylindrical cam in the cam housing;

a strand traverse guide slidable mounted on the cam housing for movement axially of the collector, the strand traverse guide engaging the cylindrical cam;

means for rotating the cam for reciprocation of the traverse guide to distribute the linear material on the package;

means for continuously sensing the angular speed of the collector as an indication of the increasing diameter of the package during collection and providing a signal proportionate to the sensed speeds, such means including a tachometer generator; and

means responsive to the sensed angular speed signal for moving the carriage away from the axial surface of the package to maintain the strand traverse in predetermined spaced relation to the axial surface of the package during formation of the package.

7. Apparatus recited in claim 6 in which the means responsive to the sensed angular speed signal includes a summing junction receiving the tachometer generator signal, a variable DC voltage source connected to the summing junction and means responsive to an unbalance voltage at the junction from the tachometer generator for both moving the carriage and changing the variable DC voltage in proportion to carriage movement until the voltage at the junction becomes balanced.

8. Apparatus for producing continuous glass filaments and for packaging strands of such filaments comprising:

means for supplying streams of molten glass for attenuation into continuous glass filaments;

means for gathering the glass filaments into a strand;

a rotatable collector for collecting the strand as a wound package;

means for rotating the collector;

means for modifying the angular speed of the collector in accordance with the changing size of the package during package formation;

la movable mounted strand traverse means for reciprocating the strand axially of the package to distribute the material on such package:

means for sensing the angular speed of the collector as an indication of the size of the package during collection; and

means responsive to the sensed angular speed for moving the strand traverse means to effectively maintain the strand traverse means in predetermined spaced relation to the package throughout package formation.

9. Apparatus for producing continuous glass filaments and for packaging strands of such filaments comprising: means for supplying streams of molten glass for attenuation into continuous glass filaments;

means for gathering the glass filaments into two strands;

co-axial rotatable collectors each for collecting one of the strands as an individual wound package;

means for rotating the collectors together;

means for modifying the angular speed of the collectors together in accordance with the Changing size of the package during collection;

a movable strand traverse means for reciprocating the glass strands axially of the packages to distribute the strands on their respective package;

means for sensing the angular speed of the collectors as an indication of the size of the packages during package formation; and

means responsive to the sensed angular speed for moving the strand traverse means to effectively maintain the strand traverse means in predetermined spaced relation to the packages throughout formation of the packages.

10. Apparatus for packaging linear material comprising:

a horizontally extending collector rotatably mounted on a fixed axis for collection of linear material as a wound package;

means for rotating the collector;

means for reducing the angular speed of the collector with the increasing diameter of the collecting package;

a carriage mounted for movement in a direction perpendicular to the axis of the collector;

a cam housing on the carriage extending in the same horizontal plane and in a direction parallel to the axis of the collector;

a rotatable cylindrical cam in the cam housing;

a strand traverse guide slidably mounted on the cam housing for movement axially of the collector in the same horizontal plant as the axis of the collector, the strand traverse guide engaging the cylindrical cam;

means for rotating the cam for reciprocation of the traverse guide to distribute the linear material on the package;

means for continuously sensing the angular speed of the collector as an indication of the increasing diameter of the package during collection and providing a signal proportionate to the sensed speeds; and

means responsive to the sensed angular speed signal for moving the carriage away from the axial surface of the package to maintain the strani traverse in predetermined spaced relation to the axial surface of the package throughout formation of the package.

11. The apparatus recited in claim 10 in which the cam housing slideably carries the strand traverse guide for movement in a direction parallel to the axis of the collector.

12. Apparatus recited in claim 11 in which the strand traverse guide includes a hooked strand engaging portion for moving the strand with it when the guide is moved away from the package during package formation.

References Cited UNITED STATES PATENTS 3,675,862 7/l972 Tsukuma 242-18 R 2,335,975 12/1943 Stahl et al. 242-18 R 2,466,600 4/1949 Lawson 242--18 R X 2,769,299 11/1956 -Keith 242-18 R X 2,972,450 2/ 1961 Brierley 242--18 R 3,371,877 3/1968 Klink et al. 242-42 X 3,549,096 12/1970 Klink 242-18 G STANLEY N. GILREATH, Primary Examiner M. S. GERSTEIN, Assistant Examiner U.S. C1. X.R. 242--18 R, 18 G, 45 

